Mining machine



March 13, 1934. F. w. VODOZ MINING MACHINE Original Filed Dec. 8, 1926 7 Sheets-Sheet 1 March 13, 1934.

F. w. VOD OZ MINING MACHINE fiven or F m W Vod 0% (/2 1 army March 13, 1934. F w VQDQZ 1,950,707

MINING MACHINE Original Filed Dec. 8. 1926 7 Sheets-Sheet 5 J4 I ZUIZiOI" -March 13, 1934. F. w. VODOZ MINING MACHINE Original Filed Dec. 8, 1926 7 Sheets-Sheet 4 March 13, 1934. w VQDQZ 1,950,707

MINING MACHINE Original Filed Dec. 8 1926 7 Sheets-Sheet 5 Ziorney/ March 13, 1934. w VQDQZ 1,950,707

MINING MACHINE Original Filed Dec. 8, 1926 7 Sheets-Sheet 6 I l L J ll March 13, 1934. w V DOZ 1,950,707

MINING MACHINE Original Filed Dec. 1926 7 Sheets-Sheet 7 I l l I l l I f- MQQM Patented Mar. 13, 1934 UNITED SATE TENT i FFIC MiNING MACHINE Frederick William- Vodoz, Wilmette, 111., assignor to Goodman Manufacturing Company, Chicago, 111., a corporation of Illinois Application December 8, 1926, Serial No. 153,253 Renewed October 3, 1931 19 Claims.

tive to the main frame for making various cuts including top or bottomslabbing cuts or side shearing cuts.

The principal object of the present invention is to produce an improved form of machine of .the class described affording a novel mounting and bearing mechanism for the cutting element whereby maximum strength and support is afforded thereto while at the same time permitting a wide range of angular movement of said arm during its various permissible cutting operations. A further object of the invention is to produce a machine especially adapted for driving entries or main passageways in a coal mine, for this purpose said machine being capable of cutting a tunnel with an arched roof.

Mining machines of the eneral type above described have been heretofore proposed and constructed in varying forms having as one of their chief characteristics a cutter head including an offset cutting element mounted at the forward end of the main frame and arranged so the entire cutter head is rotatable on 'a substantially horizontal axis extending longitudinally of the main frame. The main bearing for the cutter .head, rotatable as described, is commonly known as a neck, and is necessarily relatively massive in construction on account of the supported weight of the cutter head and cutter arm projecting beyond the neck bearing, and the enormous stresses on this bearing developed during the various cutting operations. The construction of such neck bearings is furthermore 'complicated by the provision of suitable gearing connections which usually extend therethrough for driving the cutter chain as well as producing the angular movements of the cutter bar relative to the cutter head. One of the principal difficulties, therefore, in the proper construction of min ing machines of this type is the provisionof satisfactory bearings and gearing connections for providing the necessary strength of parts, commensurate with the required flexibility of movement of the cutter arm relative to the cutter head and also the desired rotational movement of the cutter head with regard to the main frame. As will hereinafter more fully appear, I provide an improved form of bearing for the cutter head wherein the neck bearing is supplemented by an additional bearing member supported in advance of the main body of the machine and also inadvance of the main part of the cutter head itself. By means of this improved construction the strength and rigidity of the entire cutter head structure is greatly enhanced, without materially affecting the freedom'of angularmovement of the cutter'head relative to the main frame nor the angular movement of the cutter arm relative to the cutter head.-

Other objects of the invention will appear from time to time as the description proceeds.

The invention may be best understood by refer: ence to the accompanying drawings, in which:

Figure l is a side view of the machine showing the cutter bar disposed at the opposite side and proiecting forwardly from said machine, indicating in dotted lines certain other permissible positions of said cutter arm;

Figure 2 is a plan view of the machine shown in Figure l and also indicating in dotted lines other permissible positions of the cutter arm;

Figure 3 is an enlarged plan view of the machine main body with parts of the gearing mechanism shown in cross section taken on line 33 of Figure 1;

Figure 4 is a vertical section taken on .irregular line 4-4 of Figure 3;

Figure 5 is a vertical section taken on line 55 of Figure 3;

Figure- 6 is a vertical longitudinal section of the machinedrawn to a somewhat smaller scale than Figures 3, 4 and 5;

Figure 7 is an enlarged detail view or" part of the gearing reduction mechanism taken on line 7-7 of Figure 6;

Figure 3 is an enlarged sectional view of an-' other portion of the gearing reduction mechanism taken on line 8-8 of Figure 6;

Figure 9 is an enlarged detail of the reversing clutch mechanism and driving connections to the cutter head;

Figure 10 is an enlarged detail view of the drive clutch and stop for the cutter head turning mechanism taken on line l0-10 of Figure 6;

Figure 11 is a detail section taken on line 1111 of Figure 10;

Figure 12 is a detail partial sectional View of the traction driving mechanism and clutch therefor;

Figures 13 and 14 are enlarged detail views of the interchangeable chain tread or track mechanism whereby the machine frame may be either mounted on the mine tracks or propelled directly on the ground by the continuous tread de vices;

side of the machine showing the various posi' tions of the cutter arm while making a tunneling out such as is shown in Figure 17;

Figure 19 is a cross section of a modified form of cutter arm and arrangement of the cutter chain thereon for producing the arcuate cut illustrated in Figures 17 and 18.

vReferring now to the details shown in the drawings:

The main elements of the machine include a main frame 10 and a forwardly projecting cutting element 11. The machine is moved from place to place and in and out of cutting position by suitable traction means, herein comprising a pair of continuous tread mechanisms indicated generally at 13, 13, which are interchangeable with a set of track guided supporting wheels 14,

14. Means for operating and adjusting these interchangeable traction devices will hereinafter be described in greater detail.

Referring now to the cutting element and its means of connection to the main frame, the cutting element herein illustrated includes a cutter bar 15 carrying an endless cutter chain 18 mounted in a groove 16 formed around the sides and end of the cutter bar in the usual manner. The cutter bar is supported at its inner end on a cutter head indicated generally at 17. This general arrangement is illustrated in Figures 1 and 2 in which it will be seen that the cutter bar and cutter head may be bodily rotated relative to the main frame 10 on an axis extending longitudinally of the latter, as indicated in dotted lines in these figures.

The main bearings for the cutter head comprise a cylindrical neck 20 journaled in a bearing 21 formed at the front end of the main frame 10 and an auxiliary bearing member 22 journaled in a cylindrical outboard support or ring 23 connected to the main frame by a suitable rigid frame member 24 as best shown in Figures 1, 2, 4 and 5. These main cutter head bearings 21 and 23 are preferably of the split type, as for instance being divided on a horizontal plane so as to comprise base members 21 and 23 with their respective cap members 21 and 23 respectively. Said bearings 21 and 23 together form in effect trunnions for the cutter head disposed forwardly and rearwardly of the point of connection of the cutter arm and the cutter head.

The cutter arm is mounted on' the cutter head 17 for swinging movement in a plane parallel with the axis of rotation of said head in the following manner:

As seen in Figure 3 the rear end of the cutter bar 15 is provided with a hub member 25 extending inwardly and transversely of the cutter head 17. This hub portion 25 is arranged for longitudinal sliding movement in a sleeve 26 which in turn has rotational bearing in a journal 27 forming part of the cutter head 1'7. The sleeve 26 also has an integral hub extension 28 of reduced diameter disposed at the side of the cutter head opposite the cutter arm, this reduced hub portion having bearing in journal 29. As seen in Figure 3 the cutter head journals 27 and 29 appear in full lines since this view is taken at the point where these journal bearings are split on a horizontal plane. The general arrangement and construction of the bearing parts first mentioned will be understood, however, from this figure.

The sleeve 26 forms a part of the cutter arm supporting structure including a forwardly projecting arm 30 and a segment 31 carried thereby. (See Figures 2 and 3.) The arrangement is such that the cutter arm 15 with sleeve 26, arm 30 and segment 31, may be swung bodily about the common axis of the cutter arm hub 25 and sleeve 26 when power is applied through pinion 32. Power connections for the gear pinion will be hereinafter more fully described.

The cutter chain 18 is driven through a cutter chain sprocket 35 carried on shaft 36 extending through and coaxial with the cutter arm hub 25. As hereinbefore described, the cutter arm hub 25 is arranged for longitudinal sliding movement in the sleeve 26. This movement is provided for permitting limited adjustment of the entire cutter arm in planes parallel to the axis of rotation of the cutter head 17, as indicated in dotted lines in Figure 4, in which the cutter arm 15 is shown in extended position. This extended position of the cutter arm is also indicated in Figure 2 wherein the cutter arm is indicated in two permissible positions, at 15 and 15 respectively. This adjustment of the cutter arm may be controlled by any suitable means, as for example, by a screw member 38 carried at the outer end of the hub portion 28 and having internal threaded engagement with the end of shaft 36 opposite the sprocket 35. Said screw may be rotated by means of a handle 39 or its equivalent so as to shift the shaft 36 outwardly. Said shaft has suitable thrust bearings 40 in the hub member 25 which serves to carry the telescoping hub member 25 with shaft 36 in its longitudinal sliding movement and thus cause the entire cutter arm to be shifted inwardly and outwardly relative to the sleeve 26 and its associated rack 31, as desired. A guide rod 41 is preferably connected to the cutter arm 15 at a point spaced from its axis of rotation, this guide rod passing through a guide member 42 formed integral with the segment arm 30 so as to carry said cutter arm with the segment in all angular positions of the segment arm when it is operated for swinging the cutter arm on their common pivotal axes.

The cutter chain sprocket 35 and shaft 36 are driven from a beveled gear 45 which is splined or feathered on shaft 36 to permit longitudinal movement of the shaft 36 relative to said sprocket. Driving connections for said sprocket 35 will be hereinafter described in connection with the general description of all power connections for operating the machine.

From the above description it will be seen that the machine provides for three different movements of the cutter bar. In the first place the entire cutter head 17 is capable of rotation about an axis extending longitudinally of the machine so as to move the cutter bar when held in horizontal position (as shown in Figure 3) into a plurality of angular positions, the only limits of this rotational movement of the cutter bar and cutter head being that imposed by the supportfrom the main frame to provide support for the outboard bearing ring or member 23. As shown in Figure 17, however, the arrangement is such that the cutter bar and cutter head may be swung through a complete angle of approximately 270, which, as will hereinafter more fully appear, is sufficient to produce all types of cuts for which this type of mining machine is normally called upon to perform, including overcutting, undercutting and shearing cuts at either side of the machine.

It will be noted further that the cutter bar may be swung angularly about its own pivotal hub 25 in any one of the several positions to which the cutter head may be rotated, as above described.

A third permissible movement of the cutter bar is utilized only for adjusting the distance of the cutter arm from the axis of rotation of'the cutter head; this adjustment being illustrated in dotted lines in Figures 1 and 4.

Referring now to the power devices and gearing connections for producing the various cutting and positioning operations above described,

.I have shown herein a single driving motor 50 disposed at the rear end of the main frame 10, said motor as herein shown being electric and provided with an armature pinion 51. This pinion is meshed with a gear 52 and shaft 53.

A direct driving connection with the cutter chain sprocket is afforded from the front end of shaft 53 to shaft 46 which extends coaxially through the cutter head neck 20 and has a pinion 47 at the front end thereof engaging the beveled gear which has heretofore been described as the driving means for the cutter chain sprocket shaft 36. The clutch connections for this shaft are best shown in detail in Figure 9 from which it will be seen that the shafts 53 land 46 are independent of each other but sliding clutch member 48 is feathered on shaft 53 and movable into and out of driving engagement with a corresponding clutch member 4821 keyed on the rear end of shaft 46. By means of this .driving connection the cutter chain may be operated at a relatively high speed in all permissible positions of the cutter head and cutter arm.

Reversing and reduced speed connections are also provided for various operative functions of j the machine, as follows:

Shaft 53 is connected directly to a bevel gear reversing mechanism, including a pair of oppositely disposed beveled pinions 54, 54, loosely mounted on shaft 53 and selectively connectible thereto through an intermediate sliding clutch member 55. These two beveled pinions are meshed at opposite sides of a beveled gear 56 which, as shown in detail in Figure 8, is connected with a hub or sleeve 57 which forms the main driving member of a planetary gear reduction device indicated generally at 59. Such planetary gear devices are well known in the mining machine art and need not be described in detail herein excepting to point out a low speed mem- 'ber 60 having clutch jaws 61 which may be selectively engaged by clutch jaws 62 of a sliding clutch member 63 feathered on driven shaft 64 to drive the latter at a relatively low speed through the usual gear reduction devices in the Iplanetary 59. The shaft 64 is driven at a higher speed by connecting the clutch jaws 62 directly to the jawsv 65 carried at the lower end of the sleeve member 57. In this case the shaft 64 is driven at the same speed as sleeve 57 and .Jbeveled gear 56. Withthe reversing and planetary gear devices above described, it will be seen that power connections are available at a plurality of speeds and in reversible directions for several operative functions of the machine.

One of these operative functions shown herein is for operating the pinion 32, which has already been described as having driving connections with the segment 31 utilized for swinging the cutter arm at its point of pivotal connection with the cutter head 17. The gearing for this purpose may be traced as follows, starting with the shaft 64 at the lower end of the planetary device 59:

A pinion is keyed on the lower end of shaft 64 and engages the pinion 71 keyed on the shaft 72 through the idler pinion 73. (See Figures 6, 7 and 8.) At the upper end of shaft 72 is located a pair of mitre gears 75, 75, one of which is loosely mounted on the shaft 72 and selectively engageable therewith through a sliding clutch member 76. The upper mitre gear is mounted on stub shaft 77 having a pinion 78 keyed thereon which is meshed with a gear 79 keyed on sleeve 89 which projects forwardly through, and coaxially with, the neck 20, as clearly shown in Figures 3 and 6. The sleeve 80 has a gear 81 keyed thereon, which is meshed with a gear 82 on the shaft 83 extending forwardly through the neck 20 of the cutter head, but eccentric of the axis of rotation thereof, as shown in Figure 6. A worm 85 is keyed near the front end of shaft 83 and meshes with a worm gear 86 on sleeve 87, rotatable on a shaft 88. The sleeve 87 has a pinion 89 at its opposite end meshed with a gear 90 loosely mounted on a shaft 91 which carries the segment driving pinion 32 at its opposite end. A clutch member 92 affords selective driving connection between the gear 90 and the shaft 91 as desired. It will now be seen that the cutter bar 15 may be pivotally swung by power in any plane in which said cutter bar may be positioned, there being sufficient clearance at the front end of the machine for said cutter bar to swing through an angle of approximately 180. Thus, when the cutter head is rotated so the cutter bar is disposed in a substantially horizontal plane, either above or below the center of the axis of rotation of the cutter head (as shown in dotted lines in Figure 1) said cutter bar may be swung either to one side or the other of the machine so as to make a curved cut in advance of the machine, or if desired the cutter bar may be held in a fixed position to one side of the machine and the entire machine be moved along the side of a working face in a mine wall so as to make a slabbing cut therein. For this latter purpose the worm 85 and worm gear 86 are of the self locking type, that is to say, the pitch of these worms is such as to lock the cutter arm in any position to which it may be moved, as for instance, when the cutter bar is positioned for making a lateral or slabbing out, as above illustrated.

The reversible and variable speed power connections effective on driven shaft 64 to parallel shaft 72 as already described, are also utilized herein for rotating the cutter head and cutter arm bodily under power of the motor through the following train of gears:

A worm 95 is keyed on shaft 72 and is meshed with a worm gear 96 on shaft 97 as shown in dotted lines in. Figure 7. A gear 98 is keyed to shaft 97 and in turn is meshed with a gear 99 loosely mounted on stub shaft 100. These parts are best seen in Figures 7 and 10. A pinion 101 seen that by shifting the two parts 105 and 107 is keyed on shaft and is meshed with a gear wheel 102 secured to and concentric with the neck portion 20 of the cutter head 17. A clutch device shown in detail in Figure 10 is provided for selectively engaging the gear 99 with shaft 100 upon which driving pinion 101 is carried. This clutch device is also movable into another position, in which the pinion 101 is positively locked with the machine frame so as to hold the cutter head in any desired position of rotation thereof. In the form shown the clutch mechanism comprises a two-piece shifting collar, including an inner sleeve 105 feathered to shaft 100 and having clutch jaws 106 thereon adapted to engage in corresponding clutch jaws 99 in the gear 99 when said clutch member is shifted toward the left as seen in this figure. The other part of said clutch member comprises a collar 107, which is mounted on the exterior of clutch part 105 and shiftable therewith, but arranged so as to permit the latter to rotate freely therein. Said clutch part 107 is provided with a pair of laterally extending ears or lugs 108, 108, which have sliding engagement in fixed supports or guideways 109 carried by the machine frame as clearly shown in Figures 10 and 11. The part 107 is provided with a plurality of jaw members 110, 110, which may be moved to the right into engagement with recesses 111, 111 of the pinion With this clutch construction it will be as a unit toward the left, the gear 99 will be clutched to shaft 100 to form a driving connection for rotating the entire cutter head 17 on its longitudinal axis, but when shifted to the oppo- "site direction or position that is, to the right,

the clutch jaws 106 will first become disengaged from gear 99, and upon further movement the clutch jaws 110 on part 107 will become engaged in the recesses 111 formed in pinion 101, and since the part 107 is restrained from rotation by reason of the ears or lugs 108 at the sides thereof, the pinion 101 will become positively locked so as to hold the cutter head in locked position with respect to the frame.

A still further use of the power connections, through the reversing and planetary gear mechanism already described, is made for the purpose of propelling the entire machine at relatively low speeds and in reversible directions, as will now be described.

Referring to the gear 98 on stub shaft 97, as shown in Figure 7, said gear wheel is also meshed with a gear 115 keyed on shaft 116. This shaft extends rearwardly of the machine frame as shown in Figure 3 and has a gear 117 mounted on its rear end which is meshed with an idler. gear 118 which in turn is meshed with gear 119 loosely mounted on shaft 120. A sliding clutch member 121 is feathered on shaft and arranged to afford a driving connection between the gear 119 and shaft 120 in the usual manner. A beveled pinion 125 is mounted on the rear end of shaft 120 and is meshed with a beveled gear 126 on driving shaft 127 extending transversely of the rear end of the machine, as is best shown in Figure 12. A pair of sliding clutch members 128 are provided for affording selective driving connection with sprocket wheels 130, 130, at the opposite ends of the shaft, these sprocket wheels forming a driving connection with the endless low speeds. A still further power connection is afforded for propelling the machine at a higher rate of speed. These connections include gears 135, 136, and 137, affording a direct driving connection between the gear 52, meshed with armature pinion 51, and the driving shaft 120 through sliding clutch member 121, as clearly shown in Figure 6.

Referring now to the propelling mechanism including the continuous tread devices 13, 13, and the track wheel supports which are interchangeable therewith, details of this mechanism are shown in Figures 12 to 16, both inclusive. The devices at opposite sides of the machine are similar so description of one set will suffice for an understanding of both. As shown in Figure 12, the continuous tread devices shown each include the driving sprocket 130 and an endless chain tread device passing forwardly therefrom about a pair of longitudinally spaced idler sprockets and 141. These sprockets are mounted on axles 142 and 143 respectively, in position to provide sufficient clearance for the entire machine when it is being supported on the treads of the continuous chain.

Each of the track wheels 14, 14 is mounted on a disc 149 which has bearing in said wheel eccentric of the periphery thereof. Each of said discs in turn has an eccentric bearing 150 on its respective axle. The arrangement is such that the bearing 150 or discs 149 may be rotated about the axle into one position as shown in Figure 14 in which the wheels are raised out of supporting engagement with the ground, that is to say, above the normal level of the treads, of an endless chain. As a means of rotating the discs 149, 149, I provide a plurality of apertures 151, 151, about the outer periphery of said discs in position to be engaged by any suitable wrench or bar. When the discs are rotated to raised position, as shown in Figure 14, any means may be provided for locking them in place, as for instance a pivoted lug 152 may be mounted on the side of the main frame 10 in position to be inserted in one of the apertures 151 to hold the same in locked position as shown in Figure 14. Looking means are provided for securing the wheel and eccentric disc together to hold the wheel in disengagement with the ground, said means herein comprising a plunger 153 carried by each wheel and adapted to engage in a suitable recess 154 formed in a lug 155 projecting outwardly from the eccentric bearing 150 as clearly shown in Figure 15.

When it is desired to use the track wheels as a supporting and driving means, the discs are rotated to their lowermost position, as shown in Figures l3, l5 and 16, in which position the axis of the axle extending through the eccentric disc coincides with the true axis of the wheel. Locking means are provided for securing the wheel and eccentric disc in this relationship, said means herein comprising the plunger 153 carried by one wheel and adapted to engage in a suitable recess 158 formed in a lug 160 projecting outwardly from the eccentric bearing 150 as clearly shown in Figure 15. Means are also provided for affordin a driving connection between the continuous tread sprockets 140, 141, and the wheels when the latter are in supporting engagement with the track as shown in Figures 13, 15 and 16. As herein shown this connection consists of a pin 156 carried by one of the coacting members, as for instance, the wheel 14, and extending therethrough so as to be detachably connected in a chine.

suitable aperture 157 formed in the adjacent sprocket 141. By means of the above arrangement the continuous tread mechanism provides a driving connection for the wheels when the latter are in use and provides also directly the tractive effort when the wheels are raised and out of use, and the entire mechanism is supported on the treads themselves.

The use and operation of the machine above described will now be clear to one familiar with the art. The machine may be used for making an ordinary shearing cut at either side of the ma- (For this purpose the cutter bar is provided with limited adjustment laterally of the machine, as indicated in dotted lines in Figure 4.) The machine may also be used in overcutting or undercutting, or in making a slabbing out; these various cuts being produced either by maintaining the machine frame stationary and swinging the cutter bar upon its axis, or by positioning the cutter bar in a fixed position and feeding said bar by advancing the machine bodily along the track or mine bottom, or by a combination of each of these methods. The various feeding operations above discussed are well known in the art.

As to the additional feature of my invention, it will be seen that the machine illustrated herein is capable of making a new type of overhead arching out, especially designed for advancing tunnels or main entries. This cut consists of a sumping and partial shearing cut extending from the floor at one side of the machine to a position substantialy in the same horizontal plane as the axis of rotation of the cutter head. This portion of the cut is illustrated diagrammatica-L ly in Figure 18, from which it will be seen that the cutter bar is initially depressed until the front end thereof is substantially in contact with the ground and adjacent the working face at point A. The entire machine is then fed forwardly while the cutter chain is running so as to sump the machine into positon where the front end of the cutter bar reaches a new position indicated at B. The cutter bar is then raised by power of the motor so as to cut through an arc BC, in which position the cutter bar is then substantially horizontal, and disposed in substantially the same horizontal plane as the axis of rotation of the cutter head. From this position the cut is continued by locking the cutter bar in position relative to the cutter head and rotating the cutter head about through an arc CD--E as indicated in Figures 1'? and 18.

t the point E the cut is completed as a shearing cut to position F, this operation being the reverse of that used in forming the initial cut A-B-C, and the machine is finally withdrawn at the side of the room opposite the initial cut. The resulting kerf is formed in the shape of an arch having a core therein which is readily removable by the usual mining methods. This core may also be undercut by the machine to assist in its removal if desired.

In order to assist in producing the arched cut above described, I provide anovel form of cutter bar having the inner face thereof concave in cross-section as indicatedat 170 in Figure 19. By means of this arrangement suiiicient clearance for a cutter bar of standard width, and standard clearance of cutter bits, will be afforded while making the desired arched or curved cut, and thus eliminate the requirement for excessive clearances for the cutter bits resulting in an unnecessary width or thickness of the kerf,

which of course would require more power and time to produce.

t will be understood by those familiar with the art that an arched out such as above described is particularly advantageous under many conditions in coal mining operations, and especially in advancing main tunnels or entries where roof conditions are poor. It will be seen that by making an arched overcut as described, instead of the usual form of horizontal cut at the roof extending the full width of the room, the coal will be left in much more solid and substantial form so as to be practically self supporting, and thus in many cases eliminate the usual requirement for auxiliary props or support for the roof in these main entries.

Although I have shown and described one form in which my invention may be embodied, it will he understood that the construction thereof and arrangement of the various parts may be altered without departing from the spirit and scope thereof. Furthermore, I do not wish to be construed as limiting myself to the specific embodiment illustrated in the drawings, excepting as it may be limited by the appended claims.

I claim as my invention:

1. In a mining machine, a mainframe, acutter head rotatably mounted relative to said frame including a cutter offset from and mounted for pivotal swin ing movement in planes substantially parallel with the axis of rotation of said cutter head, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, and coacting power means carried by said cutter head and cutter bar for positively swinging the latter and disposed in front of said bearing.

2. In a mining machine, a main frame, a motor, a cutter head rotatably mounted relative to said frame including a cutter bar offset therefrom and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, supporting means for said cutter head including an outboard bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a gear segment carried by said cutter bar extending in front of said bearing, and gear means mounted on'said cutter head and driven by said motor for positively moving said gear segment.

3. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutter bar offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, supporting means for said cutter head includingan outboard bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a gear segment carried by said cutter bar, and gear means mounted on said cutter head and connected with said segment forwardly of said bearing for positively moving said gear segment.

In a mining machine, a frame, a motor, a cutter head rotatably mounted relative to said frame including a chain carrying cutter bar offset from and mounted for pivotal swinging movement in a plane parallel with the axis of rotation of said cutter head, power devices on said main frame, and a single set of reversing and gear reduction mechanisms affording operative connection between said motor and cutter head for operating the same and also between said motor and said cutter arm for swinging the same on its pivotal connections.

5. In a mining machine, a main frame having propelling devices therefor, a motor, a cutter head rotatably mounted relative to said frame including a chain carrying cutter bar offset from and mounted for pivotal swinging movement in a plane parallel with the axis of rotation of said cutter head, power devices on said main frame, and a single set of reversing and gear reduction mechanisms affording operative connection between said motor and cutter head for operating the same and also between said motor and said cutter arm for swinging the same on its pivotal connections, and also affording operative connection for said propelling means whereby said cutter head, cutter bar or propelling means may be selectively operated in either direction and at a plurality of speeds.

6. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, coacting power means carried by said cutter head and cutting element for positively swinging the latter, and means carried by said cutter head for varying the distance between said cutting element and the axis of rotation of said cutter head.

7. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutter bar offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, supporting means for said cutter head including an outboard bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a gear segment carried by said cutter bar, gear means mounted on said cutter head for positively moving said gear segment, and telescoping guide means forwardly of said outboard bearing, connecting said cutter bar with said cutter head in the several relative permissible positions thereof.

8. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element oifset from the axis of rotation of said cutter head and pivotally connected with the latter to swing in planes parallel with its axis of rotation, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, and power devices mounted on said frame and having operative connection with said cutter head and said cutting element, and also having operative connection to swing said cutting element relative to said cutter head, said power devices including a shaft coaxial with the axis of rotation of said cutter head, a second shaft eccentric with said first mentioned shaft and driven therefrom, and worm gear mechanism on said cutter head interposed between said second shaft and said cutting element for swinging the latter relative to said cutter head.

9. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from the axis of rotation of said cutter head, supportsegment connectible with said cutting element and projecting beyond said second mentioned bearing, and power devices mounted on said frame and having operative connection with said cutter head and said cutting element, and also having operative connection with said gear segment to swing said cutting element relative to said cutter head including a motor, a shaft journaled in said cutter head eccentric of the axis of rotation of said cutter head and geared reduction means for connecting said shaft with said motor.

10. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from the axis of rotation of said cutter head, supporting means for said cutter head including a bear-. ing adjacent the forward end of said main frame and a second bearing spaced from said main frame and beyond the point of connection of said cutter head and said cutting element, a gear segment connectible with said cutting element and projecting beyond said second mentioned bearing, power devices mounted on said frame and having operative connection with said cutter head and said cutting element and also having operative connection with said gear segment to swing said cutting element relative to said cutter head including a shaft journaled in said cutter head eccentric of the axis of rotation of said cutter head, and worm gear mechanism on said cutter head interposed between said shaft and said gear segment.

11. In'a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head and including a forwardly projecting cutter bar, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutting element and said cutter head, a motor, and coacting power means driven by said motor for positively swinging said cutting element at a plurality of speeds including a single plural speed frictionally controlled planetary gear reduction device and a gear driven therefrom disposed in front of said bearing and having driving connection with said cutting element.

12. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head and including a forwardly projecting cutter bar, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and. said cutter head, a motor, and coacting power means driven by said motor for positively swinging said cutting element at a plurality of speeds in reverse directions without reversal of said motor including reverse gearing and a planetary gear reduction device.

13. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head and including a forwardly projecting cutter bar, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a motor, and coacting power means driven by said motor for positively swinging said cutting element at a plurality of frictionally controlled speeds in reverse directions without reversal of said motor including reverse gearing and a frictionally controlled planetary gear reduction device.

14. In a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, said cutter element including a projecting cutter bar, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a motor, and coacting power means driven by said motor for positively swinging said cutting element including planetary gear reduction mechanism and a gear driven therefrom disposed in front of said bearing and having driving connection with said cutting element.

15.1n a mining machine, a main frame, a cutter head rotatably mounted relative to said frame including a cutting element offset from and mounted for pivotal swinging movement in planes substantially parallel with the axis of rotation of said cutter head, said cutting element including a projecting cutter oar, supporting means for said cutter head including a bearing spaced from said main frame and beyond the point of connection of said cutter bar and said cutter head, a motor, and coacting power means driven by said motor for selectively rotating said cutter head and swinging said cutting element including frictionally controlled planetary gear reduction mechanism.

16. In a mining machine, a main frame, a cutter head supported on said main frame for rotatable movement with respect thereto about a horizontal axis including a cutting element offset from and mounted for pivotal swinging movement with respect to said cutter head, said cutting elernent including a forwardly projecting cutter bar, a motor, and coacting power means for selectively rotating said cutter head and swinging said cutting element and cutter bar at a plurality of frictionally controlled speeds including frictionally controlled plural speed planetary gear reduction mechanism.

17. In a mining machine, a main frame, a cutter head supported on said main frame for rotatable movement with respect thereto about a horizontal axis including a cutting element off set from and mounted for pivotal swinging movement with respect to said cutter head in a plurality of planes including horizontal planes and vertical planes adjacent each side of said main frame, said cutting element including a forwardly projecting cutter bar, a motor, and coacting power means driven by said motor for selectively rotating said cutter head and positively swinging said cutting element and cutter bar at a plurality of frictionally controlled speeds in reverse directions without reversal of said motor including reverse gearing and a frictionally controlled planetary gear reduction device.

18. In a mining machine, a main frame, a cutter head supported on said main frame including a cutting element offset from and mounted for pivotal swinging movement with respect to said cutter head including a forwardly projecting cutter bar, a motor, and coacting power means for positively swinging said cutting element and cutter bar at a plurality of frictionally controlled speeds including a gear segment having connection with said cutting element and extending forwardly therefrom, a pinion disposed forwardly of said gear segment and meshing therewith and frictionally controlled plural speed gear reduction mechanism interposed between said motor and said pinion.

19. In a mining machine, a main frame, a cutter head supported on said main frame including a cutting element offset from and mounted for pivotal swinging movement with respect to said cutter head and including a forwardly projecting cutter bar, a motor, and coacting power means for positively swinging said cutting ele ment and cutter bar at a plurality of frictionally controlled speeds including a gear segment having connection with said cutter head and extending forwardly therefrom, a pinion disposed forwardly of said gear segment and meshing therewith, and frictionally controlled plural speed gear reduction mechanism interposed between said motor and said pinion including a frictionally controlled plural speed planetary gear reduction device.

FREDERICK WILLIAM VODOZ. 

